Engaging impellers pump



Nov. 8, 1949 R. J. MINSHALL ENGAGING IMPELLERS PUMP Filed Aug. 9, 1944 Nw@ uw ummm GRN

52. veraf/0 7.v er J Patented Nov. 8, 1949 ENGAGIN G IMPELLERS PUMIK Robert J. Minshall, Shaker Heights, Ohio, as-

signor, by

mesne assignments,

to Borg-Warner Corporation, Chicago, Ill., a corporation of Ililnois Application August 9, 1944, Serial No. 548,681 6 Claims. (Cl. ID3-126) The present invention relates to fluid displacement apparatus, and more particularly to pumps of the rotary type.-

It is one of the principal objects of this Vinvention to simplify the construction of a pump of the rotary type such as contemplated herein and to improve the eiiiciency, operation and dependability of lsuch pump.

Another principal object of this invention resides in providing means to prevent entrapment of iiuicl between the compressor members and thereby eliminate an objection inherent in the meshed tooth typeof gear pump.

Another object of this invention is to provide a pump wherein oppositely rotating blades are brought together in tip engagement during the final stage of the cycle of operation.

A further object is to provide a dual-chambered pump having two rotors that are provided with radially movable members such as blades for compressing the fluid and wherein a blade on one rotor is retracted by tip engagement with a yieldingly opposed member on the other rotor.

A still further object is to provide a pump wherein each compression member or blade is ported and there is a valve-control passage in the rotor adjacent each compression member that is adapted to be opened to communicate with the compression chamber for venting pressure iiuid when a predetermined pressure has been attained.

It is another object of this invention to provide a pump wherein a minimum of clearance is provided between the tive seal between the high pressure and low pressure sides of the pump.

Additional objects, aims and advantages of the invention contemplated herein will be apparent to persons skilled in the art after the construction and operation of the pump assembly is understood from the within description.

It is preferred to accomplish the numerous objects of this invention and to practice the same in the substantially the manner hereinafter fully described and as more particularly pointed out in the appended claims. Reference is now made to the accompanying drawings that form a part hereof, wherein:

Fig. 1 is a fragmentary transverse section with portions in elevation, the view being taken along the plane of line I-I on Fig. 2 andlooking in the direction of the arrows;

Fig. 2 is a longitudinal vertical section along the plane of line 2---2 on Fig. 1 looking In the direction of the arrows; and

rotors, and to eiect a posi-A other trunnion I2.

nion II is journalled I5 preferably of circular outline and .sure in a direction transverse to Fig. 3 is a fragmentary end view of a pair of compressor members or blades that have been ytildably retracted by tip engagement with each o er.

The drawings are these drawings like reference characters identify the same parts in the diiferent views.

The pump shown in the drawings comprises a by bolts or the like. The rotors 9 and I0 are The other end of the trunin a bore of a bushing plate similarly the corresponding end of the other trunnion I2 is journalled in a circular bushing plate I6.

As seen in Fig. 2 the inner faces of the bushings I3 and I4, and the corresponding inner faces of the bushings I5 and Iii-bear against the end faces of the rotors 9 and Ill. The bushings I5 and I6 are spring loaded by providing them with sockets Il and I8 respectively to receive coil compression springs I'Ia and I 8a. The outer ends of these springs press against the closure plate 8 of the shown to exert their presbushing plates I5 and I6. Thus the bushings I5 and I6 press against the rotors, which in turn are urged against the opposite bushings I3 and I4 to effect a tight fit. The bushings I5 and I6 have a snug f 'fit in the semi-cylindrical walls 5 and 6 of the compression chambers, and at the point where the peripheries of these bushing plates come into contact with each other they are provided with a transverse bore I9 into which a pin 20 is driven to eifect a seal therebetween which prevents 3 leakage from the discharge side of the pump back to the intake side thereof.

The trunnion II projects through its bearing I3 andhas a gear 2| anchored to it, and there is also a spline stub 22 projecting beyond said gear for connection with any suitable prime mover such as an corresponding end of trunnon I2 extends through the bushing I4 and has a gear 23 anchored to it that is in mesh with gear 2l. These gears 2I and 23 each have the same number of teeth so that said gears operate in synchronized relation to each other and at the same speed but in yop- ,posite directions.

As shown in the upper portion of Fig. 1, and also in the upper portion of Fig. 2, the trunnions II and I2 are hollow throughout the maior por-A tions of their lengths providing longitudinal bores X and Y that extend inward from their ends nearest the closure plate 8. of these bores are sealed by discs 24 that are forced against shouldered end portions of the bores and after the discs have been seated, the surrounding metal of the trunnions is upset as at 25 (Fig. 2) to tightly retain the discs in position and seal the ends of the trunnions.

The rotors 3 and I0 are provided with a plurality of radially disposed channels or guide slots 26 each of which has its inner portion enlarged as at 21 to provide an inner chamber. These channels 26 and their enlarged portions 2-1 extend through the ends of the rotors, and the outer portions of the channels 26 are open through the peripheries or circumferences of the respective rotors. These channels 26 receive and guide the compression members which are in the form of elongated blades or teeth 26 having chamfered or beveled outer portions 29 that are oblique to and extend away from the leading faces of the blades. The inner portions of these blades have longitudinally disposed lateral iianges 30 along their opposite edges that are adapted, when centrifugally moved outwardly by the rotation of the rotor, to engage the shoulders formed by proximate portions of the channels 26 and the enlarged inner portions 21 thereof. This arrangement insures the blades being retained in the rotor channels 26 and also permits them to move radially inward during their engagement with the cylindrical surfaces of the chambers A and B that are eccentric to the rotational axes of the rotors.

As seen in the drawings. particularly in section in Fig. 1, the blades each have a plurality of bores 3I that are radially disposed with respect to the axis of the rotor and are spaced with respect to each other transversely of the length of the blades. This affords communication between the compression chambers A and B and the inner chambers 21 that are formed by the enlarged inner portions of the guide channels 26 of the rotor.

As shown in Fig. a plurality of pockets 32 of the rotor as seen in Fig. 2. These pockets 32 constitute a plurality of passageways that register and communicate with circular or annular passageways 33 formed in the bushings I5 and I6 surrounding the trunnions II and I2 of the rotor. These passageways 33 have lateral portions 34 extending towards each other and unite in an outwardly extending common passageway between the rotors that discharges into the outlet stub 36 of the housing.

The pockets 32 communicate 1 the rotors are provided with extending lengthwise through apertures electric motor or the like. The

The Open eDdS 31 with the enlarged portions 21 of the blade guides or channels 26. These apertures are normally closed by elongated valve plates 33 that are yieldably maintained in contact with the walls of the pockets 32 by the movable arms 33 of 'hairpin shaped springs 40. The other arms 4I of these springs are anchored to the walls of the pockets opposite the valve plates 33.

As seen in Fig. -1, during the rotation oi the rotors, the blades 28 will sweep the eccentric surfaces of the compressionl chambers A and B thereby building up the pressure in front of their leading or chamfered edges 29 of said blades. During thecycle of operation the bladesA will gradually move inwardly in their guide channels 26 and the compressed iiuid will pass into the bores 3I in the respective blades and then into the enlarged portions 21 of the yguides back of the inner ends of the blades. When predetermined pressure has been attained, which is predetermined by the tension of the springs 40, the valve plates 36 will open and the pressure fluid will be vented through the apertures 31 into the pockets 32.. The pressure iiuid will leave the pockets 32 by moving into the annular passageways 33, and then pass through the lateral passageways 34 which discharge the fluid into the union passage 35 and leaves the pump through the outlet 'stub 36.

Lubrication of the moving parts is effected by means of an -elongated open-ended passageway 42 extending longitudinally in the housing wall 1 in a plane intersecting the 'axes of the rotor trunnions and communicating with annular grooves 43 and 44 in the respective bushings I3 and I4 that journal the adjacent ends of the trunnions. Diametrically opposite radial bores 45 in the trunnions are registered with the grooves 43 and 44 to lead the lubricant into the bores X and Y of the rotors. The opposite ends of the trunnions have radial bores 46 that register and communicate with annular grooves 41 in the bushings I5 and I6. Thus, the lubricant entering the trunnion bores will lubricate the end bearings of the rotors that are remote to the lubricant feed passageway 42.

While the present improvements have been described in detail in their present preferred form or embodiment, it will be apparent to persons skilled in the art, after understanding the improvements that various changes and modifications may be made therein without departing from the spirit or scope thereof. It is aimed in the appended claims to cover all such changes and modifications.

I claim:

1. A pump comprising a cylindrical wall and end members defining a compression chamber having inlet and outlet ports; a. rotor journalled for rotation in said chamber; radial guide channels in said rotor; compressor blades guided for reciprocal radial movement in said channels to operate in said chamber, said blades having means for conveying pressure fluid radially inward past said blades; longitudinal passageways in said rotor having communication with the pressure fluid conveying means in said blades, said passageways opening through an end of said rotor; valve means controlling communication between said passageways and said fluid conveying means; bushings between said chamber ends and-the adjacent ends of said rotor, spring means yieldably urging one of said bushings toward said rotor; and a passageway in one of said bushings communicating with the longitudinal passageways in said rotor for discharging the lation to a rotor journal, said annular passagepressure iiuid through said outlet port. way being arranged to receive pressure Iluid from 2. A pump comprising a cylindrical Wall and the radially inner regions of said rotor chan,- end members defining a compression chamber nels; and means in said end plate establishing having inlet and outlet ports; a rotor journalled 5 communication between said passageway and said for rotation in said chamber; radial guide outlet port. channels in said rotor having enlarged inner 5. A pump comprising a cylindrical wall and regions; blades reciprocable radially in said end plates defining a compression chamber guide channels, said blades having enlarged means dening inlet and outlet ports communiinner edges operable in the enlarged inner reeating with said compression chamber; a pair of gions of said guide channels to limit radial outradially channeled rotors journaled in said end through said blades eiective to convey pressure being arranged with. their ends engaged with said fluid to the enlarged inner regions of said end plates; blades guided for radial reciprocal guide channels; means in an end member de- 15 movement in said rotor channels and being cent end of the rotor and the outlet port; other in the inner face of the outlet end plate,

annular passageway; and valve means adapted to ing arranged to separately receive pressure Iluid control communication between said pockets and from the radially inner regions of the respective the inner regions of said guide channels. rotor channels' 3. A pump comprising a cylindrical wall and annular passageways adapted to establish comend members dening a compression chamber munication between the respective passageways having inlet and outlet ports; rotors journalled and said outlet port. for rotation in opposite directions in said cham- 6. A pump as dened in claim 5 wherein the bers; radial guide channels in said rotors, each blades have chamfered outer portions and the channel having an enlarged inner region; blades blades in one rotor are arranged to be brought reciprocable radially in said channels, said into radially aligned yieldably opposed tip enblades each having an enlarged inner edge easement with the blades of the other rotor convey pressure iiuid to said enlarged inner re- ROBERT J. MINSHALL. gions of the guide channels, means dening n passageways in an end member adjacent an end REFERENCES CITED l of each rotor and extending between said ends The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 18,986 Palmer Dec. 29, 1857 465,194 McDonald Dec. 15, 1891 723,000 Marsden Mar. 17, 1903 807,830 Leighton Dec. 19, 1905 963,690 Curtis July 5, 1910 1,185,473 Buckley May 30, 1916 1,434,716 Marion Nov. 7, 1922 1,558,696 Marlon Oct. 27, 1925 1,807,392 Davis May 26, 1931 y 2,306,276 Nash Dec. 22, 1942 *tends in close engagement with said end plates;

)blades tgouiclel for radial reciprocal movement in FOREIGN PATENTS sa d ro r c annels and being adapted to sweep said cylindrical wan. the blades in one rotor be- Nmg Greffggm Janl'femsin "ranged t0 be bm 4,266 Great Britain Feb.4,1s9z 16,011 Great Britain 1896 444,387 France 1912 528,033 GreatBritain Oct. 21, 1940 673,537 Germany Mar. 23, 1939 

